Rotary engine.



E. & T. ERIGKSON.

Patented Mar. 12, 1912.

9 SHEETS-SHEET 1.

l/vi/tweooco E. & T. ERICKSON.

ROTARY ENGINE. 7

APPLICATION FILED SEPT. 12, 1910.

Patented Mar. 12; 1912.

9 SHEETS-SHBET 2.

Erzbi'do Q vbbueooco E. 6: T. ERICKSON.

ROTARY ENGINE.

APPLICATION FILED SEPT. 12, 1910.

Patented Mar. 12,1912.

9 BHEETBBHEET 3.

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ROTARY ENGINE.

APPLICATION FILED SEPT. 12, 1910.

Patented Mar. 12, 1912.

9 SHEETS-SHEET 4.

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Patented Mar. 12, 1912.

9 SHEETS-SHEET 5.

E. & T. ERIGKSON.

ROTARY ENGINE.

APPLICATION FILED SEPT. 12, 1010.

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E. & T. ERIGKSON.

ROTARY ENGINE,

APPLICATION FILED SEPT. 12, 1910.

9 SHEBTB-SHEET 7.

Patented Mar. 12, 1912.

WWI venom E. & T. ERIOKSON.

ROTARY ENGINE.

APPLIOATION FILED SEPT. 12, 1910.

1,020,271. Patented Mar. 12, 1912.

E. & T. ERICKSON.

ROTARY ENGINE.

APPLICATION FILED SEPT. 12, 1910.

1,020,271 Patented Mar. 12, 1912.

9 SHEETS-SHEET 9.

M v anyone/13 COLUMBIA PLANOORAPH C0,. WASHINGTON. D. c.

UTTE STATES PATENT OFFICE.

EDWIN ERICKSON, OF NEAR CHANCELLOR, SOUTH DAKOTA, AND THEODORE ERIOKSON,0F JUDITH GAP, MONTANA.

ROTARY ENGINE.

T 0 all whom it may concern:

Be it known that we, EDWIN ERIOKSON and THEODORE ERIOKSON, citizens ofthe United States, residing, respectively, near Chancellor and at JudithGap, in the counties of Turner and Meagher and States of South Dakotaand Montana, have invented a new and useful Rotary Engine, of which thefollowing is a specification.

This invention relates to rotary engines of that type comprising acasing and a rotatable element within the casing, which element consistsof a plurality of radially-dis posed blades connected withoppositely-disposed frusto-conical heads that close the ends of thecasing, and a partition disk arranged obliquely to the axis of rotationand having radial slots through which the blades pass laterally back andforth during the rotation of the element to provide on each side of thedisk separate sets of compart ments or chambers between the blades, inconnection with means for supplying steam or other motive fluid intothose chambers that successively expand from zero to maximum cubicalcontents during one half of a revolution, and for exhausting the motivefluid from the same chambers as they change from maximum to minimumcubical contents, the blades inclosing each chamber being of differentareas whereby the steam acts on the blade of larger area to turn therotary element of the motor.

The invention has for one of its objects to improve and simplify theconstruction and operation of engines of this character so as to becomparatively simple and inexpensive to manufacture and keep in repair,economical in the consumption of motive fluid, capable of developinggreat power for its size and weight, and readily controlled to use livesteam at full pressure through the range of operation or through aportion thereof so as to act expansively on the blades, the arrangementof the inlet and exhaust ports being such that a single valve may beemployed for rendering the engine reversible by directing the live steamthrough one set of ports while the other set is used for exhausting.

Another object of the invention is to so design, arrange and balance theparts that friction and wear are reduced to a minimum, and by theemployment of auto1natically and constantly operated compensatingSpecification of Letters Patent.

Patented Mar. 12, 1912.

means, the parts that are subject to wear can be kept fluid-tight andthus maintained at their maximum efficiency.

Another object is the provision of a centering means serving to hold thebladedriven disk or partition plate in its oblique plane of rotation sothat excessive wear on one side or the other of the casing or disk willbe prevented, there being an indicator arranged permanently on thecasing, whereby the position of the disk may be ascertained at any timewithout disassembling the engine, to thus enable the attendant toaccurately adjust the disk through the centering means.

An additional object is to provide a novel means for counterbalancingthe lateral pressure on the blade-driven disk, due to the live steamacting thereon by utilizing the steam pressure in a simple and effectivemanner in a counterpressure chamber, in which the peripheral portion ofthe disk r0- tates, there being packing rings on the opposite sides ofthe marginal portion of the disk which provide compartments into whichfluid under pressure may be admitted to effectively oppose the pressureof the live steam utilized in rotating the movable element of the motor.

The invention has as a further object, a novel arrangement forsupporting the bladedriven disk in such a manner that leakage will beprevented and the disk will be maintained in its original position sothat wear between the casing and blades will be uniform at all points.

With these objects in view and others, as will appear as the descriptionproceeds, the invention comprises the various novel features ofconstruction and arrangement of parts which will be more fully describedhereinafter and set forth with particularity in the claims appendedhereto.

ln the accompanying drawings, which illustrate one embodiment of theinvention, Figure 1 is a front view of the engine. Fig. 2 is a rear viewthereof. Fig. 3 is a transverse section taken on line 3-3, Fig. 1. Fig.4i is a vertical longitudinal section taken on an irregular line passingthrough the body of the casing between two blades and through thecounterpressure chamber in the plane of a blade. Fig. 5 is a front viewof the rotatable structure of the motor, portions being broken away andportions being shown IIlQflIlS.

in section. Fig. 6 is a transverse section taken on a plane parallelwith the disk, and in the plane of division of the two parts of thecasing, certain of the blades being shown in section. Fig. 7 is a moreor less diagrammatic view of a modification, showing a transversesection of the engine with one set of admission ports. Fig. 8 is acentral vertical section of the fluid controlling device, the valvethereof being in elevation. F ig. 9 is a horizontal section on line 99,Fig. 8. Fig. 10 is a bottom plan view of the valve and casing, thebottom plate of the casing being removed. Fig. 11 is a perspective viewof the valve. Fig. 12 is a detail section of one set of ports in thebottom plate of the valve casing. Fig. 13 is a fragmentary perspectiveview of a portion of the bladedriven disk. Fig. 14 is a fragmentaryperspective view of one of the packing rings for the peripheral portionof the disk disposed in the counterpressure chamber. Fig. 15 is atransverse section of the counterpressure chamber and peripheralport-ion of the disk, showing the means for draining ofi the water ofcondensation from the chamber and the means for indicating the positionof the disk. Fig. 16 is a detail view of one of the blades, showing thepacking strips for the inner and outer edges thereof, together with themeans for opposing the centrifugal and gravitational forces acting onthe outer packing strip. Fig. 17 is a sectional view showing the drivingengagement between a blade and the disk. Fig. 17 is a detail sectionalviewtaken at a right angle to Fig. 17 Fig. 17 is a detail section of thevalve in the hub. Fig. 18 is a section on line 1818, Fig. 6, with theblade in elevation. Fig. 19v is a similar View showing a modification.Fig. 19 is a perspective view of one of the packing strips. Fig. 20 is atransverse section of the counterpressure chamber taken therethrough atone of the disk centering Fig. 21 is a sectional view of theself-adjusting means for the disk-supporting or bearing blocks. Fig. 22is a detail section on line 2222, Fig. 2, showing one of the joints inthe steam pipes. Fig. 23 is a diagram of the supply and exhaustconduits, together with a development of the blades and rotary disk ofthe engine for showing the system of inlet and exhaust ports.

Similar reference characters are employed to designate correspondingparts throughout the views.

Referring to the drawings, and more particularly to Figs. 1 and 2, 1designates the bed of the engine which has a central pedestal 2 thatcarries the casing A of the engine, which is of a hollow sphericalconstruction cut off transversely at its ends. The casing is made in twoparts 3 and 4, divisible on a plane disposed obliquely to the horizontalaxis. The rotatable part of the engine comprises a plurality of blades 5of 'sector form with their flat faces parallel one to the other, saidblades extending radially with respect to and in the direct-ion of thelength of the axis of rotation and connected with the blades areoppositely-arranged conical ends walls or heads 6 which have radialslots 7 for receiving the side edges of the blades, the blades and headsbeing secured together by bolts 8 passing through the heads and screwinginto the side edges of the blades, as shown clearly in Fig. 5.

Arranged within the casing is a division plate or disk 9 which iscoincident with the plane of division of the two parts of the casing;that is to say, obliquely to the axis of rotation, so that as the diskrotates with the blades, the latter will pass back and forth through thedisk whichis provided with radial slots 10 for accommodating the blades.In the present instance, six blades are shown arranged in diametricallyopposite pairs and sixty degrees apart.

The chambers between adjacent blades are divided by the obliquelyarranged disk 9 into separate live and dead steam compartments, and theblades of each live steam compartment are of different areas so that thesteam acting on the blade of larger area will turn the rotating elementof the engine. At diametrically opposite points, the disk 9 has itsopposite sides approximately in contact with the heads or end walls 6,as shown in Figs. 4 and 5, and from these points the live steam chambersuniformly increase in size during one-half revolution while the samechambers uniformly decrease in size during the second half revolution,when they become exhaust or dead steam chambers. By the particular arrangement shown, there will be three live steam compartmentscontinuously in operation on the front left half of the disk and threeadditional live steam compartments disposed diametrically opposite tothe other at the rear right half of the disk so that all the blades arepractically active during the entire revolution, whereby a powerfultorque is produced. The heads or end walls 6 are formed with hubs 11,Fig. 4, in which are keyed axially alined axles 12 that are 'journaledin bearings 13 rising from the bed 1 of the engine, and on these axlesmay be arranged a flywheel 14 and pulley 15, respectively. The casingmay be closed by end plates 16 which inclose the re'elntrant spaces inthe heads 6 to conserve the heat.

The blade-driven disk 9 is mounted in such a manner that it willmaintain its original central position and leakage, through wear, willbe prevented. For this purpose, the disk is provided with a sphericalhub 17 which is coincident with the axis of rotation and projectsequally from the opposite flat faces of the disk. The conical heads 6are provided with reentrant chambers 18 at their oppositely disposedapexes for receiving bearing blocks 19 that are concave on the sameradius as the spherical hub to fit the latter at diametrically oppositepoints in the axis ofrotation. These bearing blocks are mounted forrotation in their respective chambers or seats so that they will wearuniformly and always fit the spherical hub. The bearing blocks areconstantly urged inwardly toward each other under a pressure that willsupport the disk against its own weight. This result is accomplished bythe use of wedges 20 disposed between the blocks and the bottoms of thechambers, and threaded rods 21 mounted in the hubs of the heads 6 toexert a continuous pressure on the wedges. Each screw rod is equippedwith a spring 22 which exerts a tension to turn the rod in a directionfor moving it longitudinally toward the wedge. The outer end of thespring, as shown in Figs. 4 and 21, is fastened at 23 to the head 6 andthe inner end is connected with a collar 24. which carries a pawl 25 toengage with a ratchet wheel 26, whereby the spring can be tensioned by aspanner engaging the lugs 27 of the sleeve. Since the wedges areconstantly urged in a direction to press the bearing blocks intoengagement with the bearing ball or spherical hub 17, the wear of theparts will be compensated to thus maintain the disk 9 in its originalposition. As a result of this arrangement, the weight of the disk is notthrown upon the upper edges of the uppermost blades, as would otherwiseoccur, and wear of the grooved edges of the salne and the packing stripstherein is, therefore, avoided.

The bore of the casing is carefully finished and the outer edges of theblades are curved to correspond therewith, and extending longitudinallyof the outer edge of each blade is a curved packing strip 28 set in agroove 29, whereby the leakage of steam from one con'ipartment toanother is prevented, similar packing strips 28 being provided in theedges of the heads. These packing strips are urged outwardly under thecombined action of gravity and centrifugal "force, so that excessivefriction and wear of the casing strips would be produced, and toovercome this each strip has a counterpoise, as shown in Fig. 16. Thepacking strips 28 will, in time, wear a slight groove across the outerend of the slot in the disk. It the strip were straight with parallelsides, the changing angular relations between the disk and the bladewould cause the strip to wear a groove wi ler than itself which it wouldnot fill or bridge at most of the relative positions of the blade anddisk. Leakage would then occur along the strips at the outer ends of theslots from one side of the disk to the other side thereof, but byemploying a concave strip this leakage is prevented. Each blade 5 has atits outer end a chamber 30 into which extends a finger 31 on the packingstrip 28 that is connected by a slot and pin joint :32 with the arm 33of the counterpoise 34. which is fulcrumed at The counter-poise is soweighted with respect to the packing ring that the action oi gravity andcon tritugal force on the counterpoise will balance the action of thesame forces on the packing strip. The packing strip is urged outwardlyinto contact with the bore of the casing by springs 36 disposedequidistant from the middle of the strip and set in chambers 37 in thebottom of the packingreceiving groove 29. The inner end of each blade iscut away to form a concave seat 38 tor fitting the spherical hub of thebladedriven disk 9, and in this seat is contained an arcuate packingstrip 39 that is pressed into engagement with the spherical hub or ball17 by a spring 40 arranged behind tht' packing strip.

The blade-driven disk is provided with packings at its radial slots 10so as to prevent leakage along the blades trom the live steamcompartments to the exhaust or dead steam compartments. The constructionof this packing is disclosed in Figs. 18 and 19, and consists of aplurality of laminae or strips 41 arranged flat against each other andset in a chamber 42 extending longitudinally in each wall of the slots10 for the blades. The outer edges of the strips 11 are rounded orconvex so as to make contact with the blade in all the angular relationsof the disk with the blade, it being understood that the disk, in eachrevolution, changes from right'angular position at the end of the bladeto an oblique position at the middle of the blade. The packing stripsare all urged outwardly in any suitable manner as, for instance, in themanner hereinafter described so that each has a line contact with theblade, which latter has its opposite faces concaved so that in and outsliding movement of the packing strips as the blades pass through thedisk, will be minimized. In order to permit the blade packings to bereadily assembled, one side of the chamber 4-2 is formed by a removableplate 416 held in place by countersunk screws 17. A convenient means forurging the packing strips 41 into engagement with the blades is shown inFig. 18, whereby fluid pressure from the live steam compartments may beadmitted to the packing chambers 42. Each chamber l9. communicatesthrough a port 18 with a valve chamber 49 which communicates throughports 50 with the live steam compartment at either side of the disk.

In the valve chamber 49 is a ball &

valve 51 which moves from one end of the valve chamber to the other forclosing either port 50. When the live steam compartment is on the rightside of the disk 9, Fig. 18, the ball valve will be in position to closethe left port 50 which communicates with the exhaust or dead steamcompartment, and whilethe ball is in this position, the port 48 is incommunication with the right port 50 so that live steam can enter thepacking chamber and force the packing strips out- Wardly. After the diskmakes a half turn, the ball valve will move to the other end of thevalve chamber to connect the left port 50- with the port 48 to admitlive steam to the packing chamber from the live steam compartment, whichis now on the left side of the partition disk 9. It will thus be seenthat the packing will be held by steam pres sure against its blade.

The inner ends of the strips 41 lie normally within enlargements 42 ofthe pack ing chambers and Within said enlargement follower strips 43 arearranged around the ends of the packing strips, said follower stripsfitting closely against the sides of the packing strips and being equalthereto in length although obviously of less width. A

small space 43 is left between the follower strips and the walls of theenlargement which will receive part of the steam admitted through theport 48 so that the pres sure of the same will not only hold the packing strips against the blade but will also hold the strips 43 againstthe packing strips, thereby compensating for wear and keeping all theparts fluid tight. Leaf springs 44 are arranged between the follower orWear strips and the walls of the chamber containing the same so as toprevent the wear strips dropping away from the packing strips when thereis no fluid pressure in the packing chamber. e thus avoid the liabilityof the steam, when again admitted, entering between the packing stripsand the wear or follower-strips and forcing the latter against. thewalls of the chamber and thereby preventing the proper operation of theparts.

here steam is not admitted to the pack ing chamber, springs may be usedto hold the packing strips to the blades. In this instance, a pin 45will be fitted to each end of each packing strip and each pin will beprovided with an enlarged head 45 on which will be provided a spur 45*.A spring 45 will be coiled around this spur between the head 45 and theouter wall of the packing chamber to hold the packing strip outward andthe construction just described permits the use of a spring Wider thanthe individual strip. To compensate for wear, wedges 42 are placedagainst the packing strips be tween the same and beveled surfaces 42 ofthe packing chamber and these wedges are pressed outward by springs 42arranged between the inner ends of the same and the inner wall of thechamber.

The outer ends of the packing strips have a greater travel across theface of the blade than the inner ends thereof and, consequently, aresubject to morewear. To equalize the wear, a spring 42 see Fig. 6, maybe provided to press upon the inner end of each packing strip inaddition to the fluid pressure thereon and thus increase the pressure atthe inner end of the strip over that at the outer end thereof in anamount sufficient to equalize the wear on the strip.

The blades 5 serve to drive the disk 9 and hence a rigid drivingconnection between the blades and disk must be provided. The bladescannot drive the disk through the packing strips 41, since the latterare yielding and the blades would work back and forth in the slots ofthe disk whereby vibration or knocking would be produced. The rigiddriving connection between the blades and disk'is afforded by the meansshown in Fig. 17, in which the ball hub 17 is shown as provided with aslot 52 ar ranged transversely to the disk and registering with one ofthe slots in the disk through which the blade passes. A packing member53, in the form of a segmental plate, is arranged within the hub 17 andcarries a block 53 from which a pin 53' projects to engage a recess orsocket 54 in the inner end of the blade. After the plate 53 has beeninserted. through the slot 52, a bushing 55 is fitted over the block 53so as to properly space said plate and the blade and serve as a liningfor the slot 52, it being understood that the bushing corresponds inshape to the slot. The block 53 and pin 53 are tapered and the socket 54is frustoconical so as to facilitate the adjustment of the parts tocompensate for wear. For the same reason, the inner walls of the bushing55 converge outwardly so as to engage the sides of the block 53 at alltimes. The plate 53 is constantly urged outward against the inner edgesof the bushing and the outward pressure will be transmitted to the blockand pin so that they will automatically take up the wear and maintainsnug and fluid-tight joints with their respective seats.

We prefer to employ fluid pressure to urge the connection outwardly and,to this end, provide a valve 56 in the hub 17 to one side of the slottherein whereby steam may be admitted to the interior of the hub. Itwill be readily noted on reference to Fig. 17 that the packing plate islonger than the slot in the hub so as to cover the slot in all positionsof the blade. exposed to steam pressure within the hub is greater thanthat exposed to pressure through the slot and the plate will be held toits seat. The height of the bushing is somewhat greater than thethickness of the hub and the end of the plate 53 will, therefore, bespaced slightly from the inner wall of the hub, providing a space 56 inwhich steam will enter to balance the ends of the plate as they travelover the bushing and thereby relieve the plate of undue pressure andfriction. The devices are duplicated at diametrically opposite points,thus producing a balanced torque on the disk, and a spring 56 isarranged between the diametrically opposite plates with its endsengaging teats 56" on the inner sides of the plates so that the plateswill be held to their seats when the engine is idle or when no fluidpressure is admitted to the hub. The valve 56 is located in a chamber135 formed in the hub and having a port 136 leading to the interior ofthe hub and a port 137 leading to the space between two blades. A groove138 is formed in the inner valve seat so that the valve can notcompletely'close the inner port 136 and, consequently, steam must beadmitted to the hub whenever it is in the space between the blades,'butwhen the steam is exhausted from the chamber between the blades thepressure within the hub will force the valve to close the port 137 whichis formed in a. plug 139 secured in the outer end of the chamber 135. Aspring 1410 is arranged between this plug and the valve and bears on thevalve to lift the same when the engine comes to rest with the valve in alow position. As the steam in the hub condenses, the pressure on thevalve will be reduced and the spring then lifts the valve so that thewater of condensation will drain from the hub.

A packing strip 39' will be provided in the inner end of the blade whichis connected with the hub.

By the arrangement of the various packings described, the compartmentsbetween adjacent blades are effectively separated from each other andthe live and dead steam compartments between each pair of blades and atthe opposite sides of the blade-driven disk are separated from eachother, whereby steam economy and eflicient operation are obtained. Thesystem of conduits for admitting and exhausting steam to and from thelive and dead steam compartments is so designed that a single valve maybe employed for utilizing steam at full pressure, or expansively. Indescribing the means for admitting and exhausting motive fluid,reference is to be had to Fig. 23, which is a development of therotatable part of the motor, namely, the blades 5, heads 6, andpartition disk 9, in conection with the diagram of the fluid conduits.

In the casing are arranged ports for the admission and exhaust of steam,and these ports correspond in number to the live and dead steamcompartments. Each set of ports admits steam to the compartments at onehalf of the disk, and they will, preferably, be arranged at an angle tothe blades so that the velocity with which the steam strikes the bladewill be utilized in addition to the expansive force of the fluid, topropel the engine, The live steam ports Z, Z, Z, admit steam to thecompartments at the front left half of the disk while the live steamports Z, Z, Z", admit live steam to the compartments at the right rearhalf of the disk, and the set of exhaust ports a, e, o permit the steamto pass out from the compartments at the front right half of the disk,while the ports c, 0 6", permit the steam to pass out from thecompartments at the left rear half of the disk. The ports of each setare spaced apart approximately the same distance as the outeredges ofthe blades so that the steam entering between any two blades will be cutoff by the following blade or the blade of smaller area, so that thesteam will act on the leading blade, which is of larger area, and causethe rotary part of the engine to rotate. The live steam can be admittedsimultaneously through both ports Z and Z at diametrically oppositepoints and at opposite sides of the disk, and this steam will actexpansively after the following blades pass the inlet ports during onethird of a revolution, assuming that the ports Z, Z and Z Z, of theother set are closed. That is to say, when the blades 5, 5, reach thedotted line positions, the steam will enter the compartment-s behind thesaid blades and act on the latter to rotatethe parts in a directionindicated by the arrow, and this steam will continue to fill the saidcompartments as the latter grow larger and larger during one sixth of arevolution. until the following blades 5 5, reach the dotted lineposition, when the steam will be cut off from the said compartments toallow the steam therein to act expansively as the leading blades exposemore and more surface, until the maximum point is reached, after whichthe exhaust takes place, the compartments changing at this point fromlive to dead steam compartments. The range during which the steam actsexpansively may be shortened by also admitting steam through the portsZ, Z, by means hereinafter described, so that live steam will beadmitted during approximately one third of a revolution and expansionwill take place during approximately one sixth of a revolution. Again,steam may be admitted through the ports Z Z, in addition to the otheradmission ports, by means hereinafter described, so that the steam willact non-expansively or at maximum pressure on each blade during eachhalf revolution.

The exhaust ports are so disposed that the steam compartments may beconnected with atmosphere or a condenser at all times as thecompartments decrease from maximum to minimum size. When the live steamcompartment between the blades 5 5*, has turned through one hundred andeighty degrees, it will have reached its maximum size and will then bebrought into communication with the exhaust port 6 As it turns throughanother sixty degrees, it will communicate with the exhaust port 6, andwhatever steam has failed to pass out through the exhaust port 6 has afurther chance to escape, and during the next sixty degrees, the samecompartment will communicate with the exhaust port 6 It will thus beseen that as the compartment grows smaller and smaller, the exhauststeam has ample chance to escape, so that there will be no compressionand hence back pressure. It will thus be seen that as the compartmentsof increasing size pass successively into communication with the inletports, the live steam acts in such manner as to rotate the blades andconnected parts while simultaneously the dead steam passes out throughthe exhaust ports as the compartments of decreasing size successivelycommunicate therewith. This means that each blade is acted on by livesteam twice during each revolution, and thus power is applied at twelvepoints, since there are six blades, with the result that a substantiallyuniform torque is produced. The first inlet ports Z, Z of both sets ofcompartments are connected with the branched supply pipe p, the secondinlet ports Z, Z*, with the pipe and the third inlet ports Z Z with thepipe 19 The exhaust ports e and 6 are connected with a branched pipe 39the exhaust ports 6, 6*, with the pipe 70 and the exhaust ports 6 6 withthe pipe 29 These pipes are connected with ,a controlling valvedesignated generally by B, that has an inlet 57 and an outlet 58. Thevalve has a rotary part composed of wings 59 and 60, so arranged thatall-three exhaust pipes will be connected at one time with the outlet58, while the supply pipes p, p, 10 may be connected with the inlet 57.When the wings are in the position shown in Fig. 23, steam is admittedto the inlet ports Z, Z and the dcad steam passes out through all theexhaust ports and pipes 19 29 79 as indicated by the arrows. Since onlyone supply pipe is open, the steam acts expansively during only onethird of a revolution. By turning the wings 59 and 60 in anti-clockwisedirection, the supply pipe 9" may be'opened and also the supply pipe 0Steam would thus be admitted to the first and second inlet ports or allthree. By turning the wings 59 and 60, toa central position, the enginewill be stopped since the supply through the inlet is cut off, and byturning the wings still farther in the same direction, the ports thatwere previously used for exhausting will be converted to the inletports, and the former inlet ports will serve for exhausting, so that theengine will be reversed. The system of sup ply conduits will be the samefor a non-reversible engine, and all that is necessary to render suchengine reversible is to provide a valve such as that described, wherebyeither Set of P p 7 7 2 Z 2 P 2 y be used for supplying or exhaustingthe steam.

The construction and arrangement of the controlling valve is moreclearly set forth in Figs. 1 and 8 to 12, inclusive. It comprises acasing 61 that has a flat bottom plate 62 on which rests a rotary valvebody 63. The bottom of the valve body is carefully finished to fit onthe plate 62, which latter is provided with an exhaust port 64 and twosets of ports 65, 66, 67, and 68, 69, 7 O, that are connected,respectively, with the pipes 39, pp the bottom plate having nipples 71for connection with the various pipes. In the side of the casing is anopening 72 into which the inlet pipe is threaded.

The valve body is of circular form and of less diameter than the casing61 so as to provide an annular chamber entirely around the valve body,which communicates through a sector-shaped opening 7 3 with one or moreports of either set. The ports are arranged in close proximity so thatthe opening 73 may be brought into register with all the ports of eithergroup. At opposite sides of the opening 73 are the wings 59 and 60, soarranged that one set of ports may be brought into communication withthe exhaust port 64, while one, two or three of the other ports are opento the inlet pipe for admitting steam. The valve body has a stem 74 thatprojects out of the top of the valve casing and is equipped with ahandle 75, whereby the valve can be turned to admit steam through eitherset of ports for reversing or controlling the point of cut-01f. Thevalve body is reduced at its upper end 76 to enter a chamber 77 formedin the top of the casing, the part 76 being provided with a packing ring7 6 to snugly fit in the chamber so that the pressure of the live steamwill not act on the entire top surface of the valve body. The portion-78of the valve body, projecting beyond the part 76, is, however, exposedto the steam, whereby sufficient downward pressure will be exerted onthe valve body to maintain it seated without sufficient friction torender the turning of the valve diflicult. To hold the valve centrally,the lower end of the stem thereof engages in a stepped bearing or socket79. in the bottom plate of the valve casing.

As shown in Figs. 1 and 3, the controlling valve B is located at thefront of the machine, and the pipes ;0 0 do not extend directly to thevarious ports in the casing, but preferably the latter is cast withconduits 80, 81, 82, on the section 4 of the casing A,

and 83, S 1, 85, on the section 3 of the casing. These conduits are inthe form of belts extending partly around the respective sections of thecasing, and the lower ends of the conduits 80, 81, 82, have ports 6, e,6 respectively, shown by dotted lines, while the upper ends of theconduits 83, 84, 85, have ports Z, Z, Z, respectively, also shown bydotted lines. These conduits extend to the rear of the casing, and theconduits 80, S1, 82, as shown in Fig. 2, communicate with. the ports 6 e6 through back connecting pipes 81', 82, while the conduits 83, 84, 85,are connected with the ports Z Z", Z by back connections 83, 84;, 85.The back connections are each made in two parts connected by a joint 86which is shown in detail in Fig. 22, the joints being disposed in aplane coincident with the plane of division of the casing, so that onehalf of the back connections will be supported on one section of thecasing, and the other half of the connections with the second section ofthe casing. The joint shown in Fig. 22, comprises a coupling collar 87threaded on flanges 88 and S0 of the two parts of the back connection.The flange 89 is carried by a collar 90 threaded on one half of the backconnection so as to be removable to permit the collar 87 to beassembled. By coring out the conduits S0 to 85 in the wall of thecasing, there is less radiation of heat -from the steam than when theconduits are in the form of pipes entirely exposed at all sides.

It may be preferable, in some instances, to make the conduits as shownin Fig. 7, so that each conduit will be as long as the compartment it isintended to supply. The advantage of this arrangement is apparent whensteam is used expansively after the compartments move out ofcommunication with the inlet port, since those portions of the wall ofthe cylinder where the steam expands will be of lower temperature thanthe live steam and will thus cool the conduit through which the livesteam passes to the inlet port. In other words, it the conduit 80, Fig.7, for instance, extended half around this easing instead of the fullperipheral length of the first compartment in which live steam entersduring the full time it passes the inlet port, the expanding steam inthose compartments which are out of communication with the inlet port,will progressively fall in temperature and cool the wall of the cylindercontaining the steam supply conduit, thus materially lowering thetemperature of the incoming steam and impairing the etticiency. Theconduits 80, etc., for the different compartments, are of a length equalto one-sixth of the periphery of the casing, and each is provided with apipe 91 which stands out from the casing and is covered with asbestos soas to prevent loss of heat by radiation.

The action of the live steam in each compartment is such that a lateralpressure is exerted on the blade-driven disk and opposed end wall, aswell as the leading and "following blades. That is to say, the late 'alpressure is exerted on the disk toward the left and right at the top andbottom, as indicated by the arrows in Fig. 4, while the pressure is inthe opposite direction on the heads 0. The forces thus acting onopposite sides of each half of the disk constitute a couple tending toturn the disk on a horizontal axis disposed at right angles to the axisof rotation of the engine, as shown in Fig. t. This would tend toproduce excessive friction between the disk and the walls of acounterpressure chamber about to be described, where the disk hascontact with the latter. For overcoming this, a means is provided foropposing this couple of forces so that lateral pressure will be ml, andthe disk will rotate freely in its nominal plane without undue friction.

The casing A. is provided with an annular peripheral counterpressurechamber 92 that opens into the casing and is disposed in the same planewith the disk. This chamber is termed by flanges 03 cast on the twosections of the casing and having their meeting walls recessed to formthe chamber, the flanges being provided with peripheral ribs 0 1-through which pass bolts 07) for securing the two sections of the casingtogether. The peripheral or marginal portion of the disk rotates in thiscountcrpressm-e chamber 92. The marginal portion of the disk isctmstructed on opposite sides with two concentric ribs 90 and 97, asclearly shown in Figs. 4, 0 and 13. The ribs 97 are so located as to bedisposed within the casing, while the portion oi the disk extendingoutwardly from the ribs 97 is disposed within the annularcountel-pressure chamber. Between the ribs 00 and 07 are circulargrooves 98 and {)0 disposed immediately adjacent the respective ribs andthese grooves are connected with radial grooves 100 that are arranged inline with the blades. The segmental portions 101 at opposite sides ofthe disk and bounded by the grooves 98, 90 and 100, are countersunk withrespect to the side faces of the ribs 96 and 07. On opposite sides ofthe disk are paekings, a portion of one of the same being shown in Fig.14;. This packing comprises concentric rings 102 and 1103 con nected byradial spokes 10-t so as to form a unitary structure, and these packingsare carried by opposite sides of the peripheral portion of the disk, therings 102 and 10 3 setting in the grooves 08 and 00, respectively, andthe spokes 10 1 in the grooves 100. These rings project outwardly beyondthe ribs or flanges 00 and 07 and bear against the side walls of thecounter-pressure chamber, so that a plurality of shallow segmental compartm'ents are arranged on opposite sides of the marginal portion of thedisk. There are as many of these shallow compartments in thecounterpressure chamber as there are live and dead steam compartmentsbetween I the blades, and live steam is admit-ted to this I compartmentin such a manner as to exert a pressure on the blade-driven diskopposing that exerted by the active steam in the blade f compartments. I

The packings in the counter-pressure chamber are held in engagement withthe walls of the latter by springs 105 seated in transverse openings 106in the bottoms of the connecting grooves 100 so that the ends of thespring will engage the corresponding spokes 104 of both packings. Thedisk 9 is provided with two sets of cross passages 107 and 108 which areso arranged that each set of passages will connect the bladecompartments on one side of the disk with the counterpressurecompartments on the opp0- site side of the disk. The area of eachcounterpressure compartment is so proportioned to the area of the bladecompartment to which it is connected, that the pressure of the steam inthese compartments, acting on the disk, will be balanced. As each bladecompartment has active steam therein during one half revolution, thesteam in the connected counterpressure compartment will also be activeduring the same part of the revolution, and during the last idle half ofthe revolution, when the exhaust takes place, the steam from thecounterpressure chamber escapes through the cross passages by which itentered. It will thus be seen that at every point where live steam isacting to rotate the blades, the incidental. lateral pressure on thedisk is opposed by the steam acting in the counterpressure chamber. Thewater of condensation that might collect in the counterpressurecompartments will tend to remain therein owing to the centrifugal forceacting on the water as it is carried around by the disk. To provide anescape for this water, a drainage conduit 109 is arranged in one wall ofthe counter- I pressure chamber, as shown in Fig. 15, the receiving endof said conduit being so disposed as to communicate with the counterpressure compartments on one side of the disk as the latter rotates,while the outlet end of the conduit opens into those blade l chambersthat are connected with the exhaust. The water of condensation will thusi be drawn out through the conduits 109, especially when the engine isconnected with i the condenser. A drainage conduit 109 is arranged atdiametrically opposite sides of the engine, one for each set ofcompartments of the counterpressure chamber.

When wet steam at low temperature is I used it may be desirable to havea counterpressure chamber filled with water of condensation as the lossby condensation caused by the presence of moisture in said chamber wouldsometimes be less than the waste of steam by filling the chamber withand exhausting it of wet steam. For this purpose a valve 110, Fig. 15,is arranged to close each drainage conduit. In case superheated steam isused, it may be desirable to prevent condensation in the counterpressurechamber by keeping the walls of the latter hot through the introductionof steam in jacket spaces 111 arranged in the flanges 93, Fig. 15.

Although the tendency of the disk is to wear equally on both sides, itmight happen sometimes to wear more on one side than the other, and inorder to determine whether this condition exists, a plurality ofindicating devices 112 are arranged on the counterpressure chamber at120 degrees apart. In the peripheral face of the disk, a central groove113 is accurately cut for use in connection with these indicatingdevices. Each indicating device, as shown in Fig. 15, comprises adepressible pin 114 disposed radially in the outer wall of the counterpressure chamber so that when the disk is in central position, the pincan be depressed to engage its inner end in the peripheral groove 113.The pin is preferably made in two longitudinally divisible sections, soarranged that it can be determined which side the disk is out of true.For instance,if the wheel is inclined to the right, Fig. 15, the leftsection of the pin cannot be depressed into the groove 118, while theright section of the pin can be depressed. The position of the wheelwill thus be determined. The pin has a head 115 on its outer end, behindwhich is arranged a helical spring 116 that holds the pin outwardlyagainst a stop bracket 117. The indicating device is thus alwaysavailable and can be used while the engine is operating to ascertain theposition of the disk. In connection with these inclicatingdevices,adjustable devices 118 are employed for truing or centering the disk. Asshown in Fig. 20, each disk centering device comprises a pair ofslidable shoes 119 extending inwardly from opposite sides of thecounterpressure chamber through openings 120 so as to engage the sidefaces of the outer peripheral ribs 96 on the disk. These shoes or guidemembers are constantly urged inwardly toward each other so as to take upwear between them and the disk, but are prevented from moving outwardly,so that when once adjusted, they will hold the disk in central positionunless the latter wears more on one side than the other.

The members 119 have upwardly-extending arms or brackets 121 terminatingin internally threaded sleeves 122, through which passes a rod 123 thathas right and left-hand threads engaging, respectively, in the sleeves122 of the shoes. Thus, by turning the screw in one direction, the shoeswill be moved inwardly toward the disk. This turning may be effected bya device 12 1 similar to the spring device 22, Fig. 4, for tighteningthe bearing blocks 19 which support the disk. It may be desirable tomove both shoes together in one direction or the other for placing thedisk in its true or central position. For this purpose, an adjusting nut125 is arranged on the rod 123 between the shoulders 126 and 127, andthis nut screws into an opening 128 in one of the ribs 9% of thecounterpressure chamber. Thus, by turning the nut in one direction orthe other, the rod 123 will be moved longitudinally and carry thedisk-engaging shoes or devices with it. The shoulder 127 is formed by asleeve 129 on which the right hand threads are cut, and this sleeve isheld rigid on the rod 123 by a jam nut 130. One end of the rod issquared at 131 so as to be held by a wrench, while the nut 125 isturned.

Since the inner ribs 97 on the disk, Figs. 1

and 13, are disposed within the casing, they are cut away at points inline with the blade-receivin slots of the disk so that the blades canride back and forth therethrough while maintaining contact with the boreof the casing. The packing strips of the blades will thus ride on theinner rings 103 of the packings in the counterpressure chan'iber and inthe outer ends of the blade-receiving slots. The heads 6 have theirinner faces provided with an annular recess 131, Fig.

4, at the perlpheral edges so as to provide grooves immediately adjacentthe casing for accommodating the inner ribs 97. By thus recessing theheads, the area of contact between the periphery thereof with the casingis reduced so that leakage of fluid is more apt to occur, and to preventthis leakage, packing rings 132 are inserted between the heads andeasing. These rings are wedgeshaped in cross section and are pressedinwardly by springs 13 1, as clearly shown in Fig. 1. By removing theend plates 16, the packings can be taken out and renewed when required.

It is customary in rotary engine practice to employ two rotatableelements or rotors mounted upon the same shaft in order that one maybalance the other, and the same practice may be followed in connectionwith the structure hereinbefore described.

From the foregoing description, taken in connection with theaccompanying drawings, the advantages of the construction and of themethod of operation will be readily apparent to those skilled in the artto which the invention appertains, and while we have described theprinciple of operation of the invention, together with the apparatuswhich we now consider to be the best embodiment thereof, we desire tohave it understood that the apparatus shown is merely illustrative, andthat such changes may be made when desired as are within the scope ofthe claims appended hereto.

Having thus described the invention, what we claim as new, and desire tosecure by Letters Patent, i

1. In a rotary engine, the combination of a casing, a rotatable diskdisposed in the easing obliquely to the axis of rotation, a

plurality of spaced blades mounted with respect to the disk for relativelateral movement therethrough and cooperating with the disk to provideseparate sets of compartments at opposite sides of the disk whichincrease from minimum to maximum size during different portions of arevolution, means for supplying motive fluid to the compartments atsuccessive points in the revolution of each compartment, and means forrendering the supply means active during the initial part of orthroughout the range of the increase of the compartments from minimum tomaximum size.

2. In a rotary engine, the combination of a casing, a plurality ofradially disposed blades mounted for rotation in the casing, a bladedriven disk mounted obliquely to the axis of rotation and through whichthe blades have lateral movement, said blades and disk cooperating toform sets of live steam compartments on opposite sides of the disk atdiagonally opposite points and sets of dead steam con'ipartments onopposite sides of the disk at other diagonally opposite points, meansfor simultaneously supplying motive fluid to the first set ofcompartments, said means being distributed to different points in thepath of increase of the compartments from minimum to maximum size, andmeans for supplying motive fluid through any predetermined ones of thedistributed supply means on the increase of the compartments fromminimum to maximum size.

3. In a rotary engine, the combination of a casing, a plurality ofrotatable blades disposed in radial relation thereto, a disk mounted torotate on an axis coincident with the blades and disposed in a planeoblique to the axis of rotation, said blades being movable laterallythrough the disk and cooperating with the latter to provide separatesets of expanding and contracting compartments, fluid supply portsspaced around the casing and corresponding in number to the expandingcompartments, exhaust ports spaced around the casing and correspondingin number to the contracting compartments, and means for controlling theadmission of fluid through the first named ports to enter the successivecompartments during the initial part of or throughout the range of theirincrease from minimum to maximum size, and for the exhaust of fluid fromthe second named ports.

4. In a rotary engine, the combination of a casing, a plurality ofradial blades mounted for rotation therein, a disk mounted obliquely tothe axis of rotation and through which the blades move laterally, saidblades and disk cooperating to form compartments at each side of thedisk successively increasing from minimum to maxi-- mum size duringone-half the revolution and decreasing from the maximum to minimum sizeduring the successive half revolution, conduits equal in number to thecompartments and connected with the casing at spaced points forcommunication with said compartments, and a common valve controlling thepassage of fluid through the conduits and constructed to admit fluid tothose compartments increasing in size on both sides of the disk during apart, or throughout the period of increase in size and for connectingthe compartments of decreasing size with the exhaust.

5. In a rotary engine, the combination of a blade-driven disk disposedobliquely to the axis of rotation, blade compartments at opposite sidesof the disk, a counterpressure chamber extending around the casing inwhich the marginal portion of the disk moves, means for dividing thechamber at opposite sides of the disk into the same number ofcompartments as there are blade compartments, means for admitting fluidfrom the blade compartments at one side of the disk to thecounterpressure compartments at the opposite side of the disk, and meansfor draining the water of condensation from the counterpressurecompartments.

6. In a rotary engine, the combination of a casing, a plurality ofradially-disposed blades rotatably mounted therein, an obliquelyarranged partition disk driven by the blades, a counterpressure chamberextending around the casing and in which the peripheral portion of thedisk rotates, de vices on opposite sides 01": the disk and rotatabletherewith for forming a plurality of counterpressure compartments ofconstantarea, there being one counterpressure compartment for each bladecompartment, and means of communication between each blade compartmentand its respective counterpressure compartment.

7 In a rotary engine, the combination of a casing, a plurality of bladestherein, a partition disk disposed obliquely to the axis of rotation andcooperating with the blades for forming a plurality of compartments, anannular chamber extending around the periphery of the casing and inwhich the peripheral portion of the disk rotates, said chamber havingflat opposed walls, packings carried by opposite sides of the disk andengaging the fiat walls of the chamber,

said packings being provided with a plurality of counterpressurecompartments, and means for admitting fluid under pressure to thosecompartments that are opposite the blade compartments that contain fluidunder pressure for opposing the lateral pressure exerted by such fluidon the disk.

8. In a rotary engine, the combination of a casing, a plurality ofblades therein, a partition disk disposed obliquely to the axis ofrotation and cooperating with the blades for forming a plurality ofcompartments, an annular chamber extending around the periphery of thecasing and in which the peripheral portion of the disk rotates, saidchamber having flat opposed walls, packings carried by opposite sides ofthe disk and engaging the flat Walls of the chamber, said packings beingprovided with a plurality of counterpressure compartments, means foradmitting fluid under pressure to those compartments that are oppositethe blade compartments that contain fluid under pressure for opposingthe lateral pressure exerted by such fluid on the disk, and meanscarried by the disk for holding both against the walls of said chamber,

9. In an engine, the combination of a casing, a peripheral chamberextending around the same and disposed obliquely to the axis of thecasing, the casing for rotation with its peripheral portion disposed inthe chamber, blades in the casing movable laterally through thepartition disk for driving the latter, annular packings disposed in thechamber at opposite sides of the disk and rotatable therewith, eachpacking having as many fluid-tight compartments as there arecompartments between the blades, and means carried by the disk foradmitting fluid under pressure to the packing compartments disposed onopposite sides of the disk from the blade compartments containing fluidunder pressure.

10. In a rotary engine, the combination of a casing, an annular chamberextending around the same and disposed in a plane obliquely to the axisof rotation, a disk mounted in the casing with its peripheral portionrotating in the chamber, blades in the casing for driving the ,disk, theopposite sides of the disk at its peripheral portion being provided withspaced annular grooves connected by radial grooves, packing ringsmounted on each side of the disk and seated in the grooves, means forurging the packings outwardly into engagement with the opposed walls ofthe said chamber, the packing rings being provided with counterpressurecompartments each connected with a compartment between the blades foradmitting fluid under pressure packings a partition disk mounted in inthe casing for driving the disk and cooperating therewith for formingblade compartments, said peripheral portion of the disk being providedon opposite sides with concentric grooves connected with radial grooves,the radial grooves being disposed in alinement with the blades, packingsarranged at opposite sides of the disk and each consistlng of concentricrings connectpartments,

ed by radial ribs for seating in the grooves of the disk, and means foracting on both packings for urging the same outwardly into engagementwith the walls of the chamber, said packings forming counterpressurecompartments for the respective blade compartments, and means foradmitting fluid under pressure to the counterpressure compartments tooppose the lateral pressure on the disk from the active motive fluid inthe blade compartments.

12. In a rotary engine, the combination of a casing, an annular chamberextending around the same, a blade driven disk disposed in the casingwith its peripheral portion rotating in the chamber, concentric ribsextending from opposite sides of the peripheral portion of the disk,means for dividing the space between the ribs into counterpressurecompartments, and means for admitting and exhausting fluid to and fromthe counterpressure compartments in such manner as to counterbalance thepressure of the motive fluid in the casing acting on the disk.

13. In a rotary engine, the combination of a casing, a chamber extendingaround the same and opening into the casing, a bladedriven partitiondisk mounted in the casing with its peripheral portion rotatable in thechamber, laterally-movable packings on opposite sides of and carried bythe disk for cooperating with the opposed walls of the chamber forforming counterpressure commeans for admitting fluid to and from thecompartments for opposing the pressure of the motive fluid in the casingacting on the disk, and a plurality of devices spaced around thepackings for urging the latter outwardly into contact with the walls ofthe chamber.

14. In a rotary engine, the combination of a casing, an annular chamberextending around the same, an obliquely arranged rotary disk in thecasing having its peripheral portion rotatable in the chamber, packingsdisposed in the chamber at opposite sides of the disk, means on the diskfor holding the packings in concentric relation to the latter, separatemeans for preventing independent rotation of the packings on the disk,means for urging the packings into engagement with the walls of thechamber to form a plurality of independent counterpressure compartmentsat opposite sides of the disk, means for admitting fluid under pressureto the compartments at such points in the rotation of the disk as tocounterbalance the lateral pressure on the disk from the motive fluid inthe casing, and means for exhausting the fluid from the counterpressurecompartments at those points where the motive fluid is exhausted fromthe casing.

15. In a rotary engine, the combination of a casing, an annular chamberextending around the same, a blade-driven disk mounted in the casingwith its peripheral portion disposed in the chamber, means for dividingthe space in the chamber at opposite sides of the disk intocounterpressure compartments, means for admitting fluid under pressureto the compartments for opposing the lateral pressure of the motivefluid in the casing on the disk, and a controllable means for thecounterpressure compartments of each side of the disk for draining thewater of condensation therefrom.

16. In a rotary engine, the combination of a casing, an annular chamberextending around the same, a blade-driven disk mounted in the casingwith its peripheral portion disposed in the chamber, means for dividingthe space in the chamber at opposite sides of the disk intocounterpressure compartments, means for admitting fluid under pressureto the compartments for opposing the lateral pressure of the motivefluid in the casing on the disk, and heating means in the walls of thechamber in operative relation to the counterpressure compartments tocounteract the tendency of the motive fluid to condense.

17. In a rotary engine, the combination of a casing, an obliquelyarranged blade-driven disk mounted in the casing, and means on thecasing for ascertaining the posit-ion of the disk.

18. In a rotary engine, the combination of a casing, an obliquely ar'anged blade-driven disk mounted in the casing, said disk having spacedwalls in its periphery, and an indicating device cooperating with thesaid walls for determining the position of the disk.

19. In a rotary engine, the combination of a casing, an obliquelyarranged blade-driven disk mounted in the casing, said disk havingspaced walls in its periphery, and an indicating device cooperating withthe said

